Electric drive for a motor vehicle

ABSTRACT

An electric drive for a motor vehicle comprising an electric motor and a drive unit is disclosed. The drive unit has a first gear stage, driveable by the electric motor, a second gear stage, driveable by the first gear stage, and a differential drive, driveable by the second gear stage. The first gear stage has a driving wheel and an output wheel, wherein the driving wheel is arranged coaxially to the output shaft of the electric motor and is rotatingly driveable by the electric motor around a first rotational axis A. The output wheel is drivingly connected to the driving wheel and is rotatingly driveable around a second rotational axis B, wherein the second rotational axis B is arranged parallel off-set to the first rotational axis A. The second gear stage and the differential drive are arranged coaxially to the second rotational axis B.

TECHNICAL FIELD

The disclosure relates to an electric drive for a motor vehicle as wellas a motor vehicle with such an electric drive. The electric drive canserve as an exclusive drive for the motor vehicle or, additionally, acombustion engine can be provided. In this case, the electric drive andthe combustion engine can drive the vehicle, respectively, on their ownor together superimposed. Such drive concepts are also designated as“hybrid drives”.

BACKGROUND

Usually, an electric drive comprises an electric motor as well as areduction drive arranged downstream that reduces the rotational movementproduced by the electric motor, from faster to slower. The torque istransmitted from the reduction drive to the drive line of the motorvehicle. For this, a differential drive, which is arranged downstream inthe torque flow of the reduction drive, splits the introduced torqueonto two output shafts for driving the wheels. The two output shafts ofthe differential drive have a balancing effect on each other, i.e., ifone of the two output shafts rotates faster, then the other of the twooutput shafts rotates correspondingly slower, and vice versa.

From U.S. Pat. No. 7,497,286 B2 an electric drive for driving a motorvehicle is known. The electric drive comprises an electric motor, aplanetary drive as a reduction drive and a differential drive, which isarranged downstream of the reduction drive in the torque flow. Theplanetary drive and the differential drive are arranged coaxially andwithin the electric motor. The sun gear of the planetary drive is drivenby the electric motor. The planet carrier is supported and the ring geardrives the differential carrier of the differential drive.

From DE 20 2005 019 438 U1 a drive unit is known, in which the electricmotor is arranged coaxially to the differential drive. A speed reductionis achieved via a gear stage on a countershaft. On the countershaft, ashift drive is provided, which has two gear stages and is shiftable viatwo switching clutches.

From DE 100 02 133 B4 a hybrid drive for a motor vehicle is known, inwhich an electric motor and a planetary drive are arranged coaxially toeach other. The force transmission onto the axle off-set differentialdrive is achieved by means of a belt drive via a continuously variabledrive as well as a clutch.

SUMMARY

The integration of an electric drive or hybrid drive, respectively, witha downstream arranged reduction drive is very often difficult, becauseof an available space, which is very tightly dimensioned.

An electric drive for a motor vehicle is proposed herein, wherein theelectric drive comprises an electric motor and a drive unit. The driveunit has a first gear stage, driveable by the electric motor, a secondgear stage, driveable by the first gear stage and a differential drive,driveable by the second gear stage, wherein the first gear stage has adriving wheel and an output wheel, wherein the driving wheel is arrangedcoaxially to an output shaft of the electric motor and is rotatinglydriveable by the electric motor around a first rotational axis, andwherein the output wheel is drivingly connected to the driving wheel andis driveable rotatingly around a second rotational axis. The secondrotational axis is arranged parallel off-set to the first rotationalaxis. The second gear stage and the differential drive are arrangedcoaxially to the second rotational axis.

The disclosed electric drive advantageously has a compact configuration.This is, the axle-offset existing between the rotational axis of theelectric motor and the second rotational axis of the second gear stageis used by the first gear stage to produce a reduction to the slowerspeed. Furthermore, it is advantageous concerning the configurationspace that the second gear stage and the differential drive are arrangedcoaxially to each other. As the planetary drive and the differentialdrive are arranged coaxially to each other or to the second rotationalaxis, the drive unit has a small radial configuration size.

The electric drive may be suitable as an exclusive drive for a motorvehicle or as an additional drive source in a motor vehicle, which has acombustion engine as the main drive source, which are also designated ashybrid drives. The electric drive can be used for driving any driveaxle, i.e. front axle as well as rear axle.

According to one exemplary embodiment, the first gear stage comprises areduction drive, which produces a transmission to a slower speed. Thus,the input element of the second gear stage rotates slower than theoutput wheel of the first gear stage. The gear stage can have a beltdrive or a chain drive or a spur gear drive. In this case, the use of abelt drive has an advantage, in that the first gear stage can run dry,i.e. a lubrication of only the second gear stage or the differentialdrive is necessary. In the embodiment with a belt drive, the drive wheelis a first belt pulley with a smaller diameter and the output wheel is asecond belt pulley with a larger diameter. In this case, the first andsecond belt pulleys are drivingly connected via a continuous belt toeach other. When using a chain drive, the configuration is similar. Thedrive wheel is a small sprocket, the output wheel is a sprocket withlarger diameter. The two sprockets are drivingly connected via acontinuous chain for the transmission of a torque to each other. Whenusing a spur gear drive as a first gear stage, the first driving wheeland the second driving wheel are drivingly connected by direct toothmeshing or via further interconnected toothed gears to each other forthe transmission of a torque.

According to another exemplary configuration, the second gear stagecomprises at least a planetary drive with a ring gear, a sun gear, amultitude of planetary gears as well as a planet carrier. The ring gear,the sun gear and the planet carrier are arranged coaxially to the secondrotational axis. The planetary gears are rotatably supported on theplanet carrier and rotate therewith together around the secondrotational axis. In this case, the planetary gears mesh, respectively,with the sun gear and the ring gear. In one exemplary configuration, oneof the gears, the sun gear or the ring gear, is drivingly connected tothe output wheel of the first gear stage, while the other of the twogears, the ring gear or the sun gear, is support or supportable on astationary component. The output element of the planetary drive serves aplanet carrier, which is connected to the differential carrier fortransmitting a torque.

The stationary component can, for example, be a drive housing or acomponent connected thereto. For the torque transmission between theoutput wheel of the first gear stage and the input wheel of the secondgear stage, a hollow shaft can, for example, be interconnected, which isarranged coaxially to the second rotational axis and through which aside shaft of the motor vehicle, driven by the differential drive, ispassed. An especially compact configuration is achieved with a directtorque flow, if the torque is introduced via the sun gear into theplanetary drive and if the ring gear is support or supportable on thestationary component.

The ring gear can be permanently connected and rotationally fixed to thestationary component, which is also designated as supported, or the ringgear can be selectively connected and rotationally fixed to thestationary component and can be disconnected therefrom, which is alsodesignated as supportable. This releasable rotationally fixed connectioncan, for example, be achieved by a clutch, which is arranged in thepower path between the ring gear and the stationary component.

The differential drive comprises several differential gears rotatablysupported in the differential carrier, which rotate together with thedifferential carrier around the rotational axis, as well as two sideshaft gears, which are rotatably supported coaxially to the rotationalaxis and which mesh with the differential gears. For a compactconfiguration, it is advantageous if the planetary drive is arrangedaxially next to the differential carrier.

According to a further exemplary embodiment, an external controllableclutch assembly can be provided, which may be arranged between the ringgear of the planetary drive and the stationary component. The clutchassembly is formed such, that, selectively, a torque can be transmittedbetween the ring gear and the stationary component or the torquetransmission can be interrupted. The clutch assembly can, in principle,be arranged at any position in the power path between the ring gear andthe stationary component. For actuating the clutch assembly, at leastone external controllable actuating device is provided. The actuatingdevice is controlled according to one exemplary embodiment by theelectronic control unit of the motor vehicle. A flexible torqueintroduction or a change of the transmission ratio is achieved in anadvantageous manner by the use of the clutch assembly.

According to another exemplary arrangement, with a clutch, the planetarydrive comprises two planetary gear stages, which are arranged,function-wise, parallel to each other and have a different transmissionratio, i.e. the first planetary gear stage has a first transmissionratio and the second planetary gear stage has a second transmissionratio between the input element and the output element. By thisarrangement, it is achieved in an advantageous manner, that the torqueintroduced into the planetary drive is selectively transmitted onto thedifferential drive via the first planetary gear stage, so that thedifferential carrier is driven with a first number of revolutions or viathe second planetary gear stage, so that the differential carrier isdriven with a different second number of revolutions. The two planetarygear stages comprise each a sun gear, a ring gear, a multitude ofplanetary gears and a planet carrier, on which the planetary gears arerotatably supported. The gears of the first planetary stage aredesignated in the following also as first gears and the gears of thesecond planetary stage are also designated as second gears.

The first and the second sun gear are connected so as to be rotationallyfixed to each other, so that they rotate with the same number ofrevolutions around the second rotational axis. The first and secondplanetary gears are connected correspondingly to the planet carrier,respectively the differential carrier, so that they rotate togethertherewith. The first and second ring gear can, selectively, be supportedon the stationary component against rotation and can be releasedtherefrom.

The clutch assembly can have different embodiments. For example, theclutch assembly may comprise one or more switching clutches, whichachieve, especially, by form-fitting means, a torque transmissionbetween a first clutch element and a second clutch element. For example,a denture clutch or a claw clutch can be used. The clutch assembly canalso comprise one or more friction clutches, which carry out a torquetransmission by force transmission. The friction clutches have theadvantage, that the torque transmission between the open position, inwhich no torque is transmitted, and a closed position, in which the fulltorque is transmitted between the clutch input element and the clutchoutput element, is variably adjustable also in any intermediateposition.

In the embodiment in which the clutch assembly comprises at least oneswitching clutch, the switching clutch is transferable at least into afirst switching position and into a second switching position. In thefirst switching position, the first ring gear is connected so as to berotationally fixed to the stationary component and the second ring gearis freely rotatable relative to the stationary component. Vice versa, inthe second switching position of the switching clutch, the first ringgear is freely rotatable relative to the stationary component, while thesecond ring gear is connected so as to be rotationally fixed to thestationary component for the transmission of a torque. By means ofswitching the switching clutch into the first or second position,different transmission ratios of the planetary drive can be achieved,for example a transmission ratio of the planetary drive, which issmaller than 20, i.e. i1<20, and a smaller second transmission ratio,which, depending on the number of teeth of the gears, can, for example,be between 8 and 15, i.e. i2=8−15. When using a friction clutch insteadof a switching clutch, the transmission ratio would also be freelyadjustable in the intermediate ranges between the first and the secondtransmission ratio. The switching clutch may be additionallytransferable into a third switching position, in which the first ringgear and the second ring gear are freely rotatable relative to thestationary component.

For the highest degree of flexibility concerning the adjustment of theto be transmitted torque, it is advantageous, when the clutch assemblycomprises a first friction clutch, which is arranged between the firstring gear and the stationary component, and a second friction clutch,which is arranged between the second ring gear and the stationarycomponent. In this case, it is, especially, provided, that the first andthe second friction clutch, respectively, are variably controllablebetween an open position, in which the torque transmission isinterrupted, and a closed position, in which the torque is transmitted.In one exemplary arrangement, the friction clutches are formed asfriction disk clutches. The friction disk clutches comprise,respectively, a first clutch element, with which the first disks areconnected rotationally fixed, and a second clutch element, with whichthe second disks are connected rotationally fixed. In this case, thefirst and second disks are arranged axially alternatingly and formtogether a disk pack.

According to another embodiment, a separate actuating devices isprovided for each one of the first and for the second friction clutch,which can actuate individually the corresponding friction clutch. Thetwo actuating devices may be selectively controlled by an electroniccontrol unit.

The electric drive can have one or more of the above named embodiments.The electric drive does provide an advantage for motor vehicles in thatonly a small configuration space has to be provided. By using a clutchassembly or a multitude of planetary gear stages, different transmissionratios can be produced, which can be adapted to the requirements of themotor vehicle drive.

DETAILED DESCRIPTION OF THE DRAWINGS

Exemplary embodiments are described in the following using the drawingfigures, wherein:

FIG. 1 schematically illustrates an electric drive according to a firstembodiment having a belt drive,

FIG. 2 schematically illustrates an electric drive according to a secondembodiment having a chain drive,

FIG. 3 schematically illustrates an electric drive according to a thirdembodiment with a spur gear drive,

FIG. 4 schematically illustrates an electric drive according to a fourthembodiment with a belt drive and a switchable planetary drive,

FIG. 5 schematically illustrates an electric drive according to a fifthembodiment with a chain drive and a switchable planetary drive,

FIG. 6 schematically illustrates an electric drive according to a sixthembodiment with a spur gear drive and a switchable planetary drive.

DETAILED DESCRIPTION

FIG. 1 shows an electric drive 2 according to a first embodiment. Theelectric drive 2 comprises an electric motor 3 and a drive unit 4, whichtransmits the torque introduced by the electric motor 3 onto two sideshafts 5, 6. The drive unit 4 comprises a first gear stage 7, a secondgear stage 8 and a third gear stage 9, which is formed as a differentialdrive. It is visible, that the electric motor 3 and the differentialdrive 9 are arranged off-set at a distance to each other.

The first gear stage 7 comprises in the present embodiment according toFIG. 1 a belt drive arrangement with a driving wheel 10 and an outputwheel 12, which is driven via a continuous belt 13 by the driving wheel10. It is visible, that the output wheel 12 has an essentially largerdiameter than the driving wheel 10, so that here a transmission to theslower is achieved. The axle off-set between the electric motor 3 andthe planetary drive 8 or the differential drive 9 is bridged by thefirst gear stage 7.

The driving wheel 10 is rotatingly driven by the output shaft of theelectric motor 3 around a first rotational axis A. The output wheel 12,which is rotatingly driven by the belt 13, is connected in a fixedmanner to a hollow shaft 24, which is rotatably supported by first andsecond bearing arrangements 15, 16 in a stationary housing 17 of thedrive unit 4. The annular chamber between the stationary housing 17 andthe rotatingly driveable hollow shaft 24 is sealed by suitable sealingelements 18, 18′, such as, for example, radial shaft sealing rings.Thus, it is prevented, that lubricant, which serves for lubricating andcooling the planetary drive 8 and the differential drive 9, gets intothe inner chamber of the first gear stage 7. The housing portion 11 ofthe stationary housing 17, in which the belt drive is arranged, is dry,as no lubrication is necessary for the belt drive. In contrast thereto,the second housing portion 14, in which the planetary drive 8 and thedifferential drive 9 are accommodated, is filled with lubricant. Theannular chamber between the side shafts 5, 6 and the stationary housing17 or the sleeve lugs of the housing 17 is sealed by suitable sealingelements 21, 21′, which can, for example, be in the form of radial shaftseal rings.

Within the housing portion 14, the planetary drive 8 and thedifferential drive 9 are accommodated. The planetary drive comprises asun gear 20, which is connected in a fixed manner to the hollow shaft 24and rotates therewith around a second rotational axis B, a ring gear 19,which is arranged coaxially to the sun gear 20 and is connectedrotationally fixed to the housing 17, a multitude of planetary gears 22,which mesh with the ring gear 19 and the sun gear 20, as well as aplanet carrier 23. The planet carrier 23 is arranged coaxially to therotational axis B and transmits the torque introduced into the planetarygear 8 onto the differential drive 9. The ring gear 19 is fixedinternally on the housing 17, for example is welded or screwed thereto.The drive is achieved in this case from the hollow shaft 24 via the sungear 20 and the planetary gears 22 onto the planet carrier 23. However,also an embodiment is, in principle, possible, in which the ring gear isdriveable by the shaft, while the sun gear is supported against rotationon a stationary component, for example on a housing.

The differential drive 9 comprises a differential carrier 26, which isconnected in a fixed manner to the planet carrier 23 and is rotatinglydriveable by the same around the rotational axis B, a multitude ofdifferential gears 27, which are rotatably supported in the differentialcarrier 26 on the rotational axes and rotate together with thedifferential carrier 26 around the rotational axis B, as well as twoside shaft gears 28, 29, which each are rotatably arranged coaxially tothe rotational axis B and mesh with the differential gears 27. Thedifferential carrier 26 is rotatably supported via the bearingarrangements 16, 30 in the housing 17 around the rotational axis B. Thetorque introduced into the differential carrier 26 is transmitted viathe differential gears 27 onto both side shaft gears 28, 29, wherein abalancing effect exists between the two side shaft gears 28, 29. Theside shaft gears 28, 29 are again connected for the transmission of atorque rotationally fixed to the corresponding side shafts 5, 6, whichtransmit the introduced torque onto the wheels of the motor vehicle.

It is visible, that the planet carrier 23 of the planetary drive 8 isconnected in a fixed manner to the differential carrier 26 of thedifferential drive 9, i.e. the planet carrier 23 forms the outputelement of the planetary drive 8, by means of which the torque isintroduced by the planetary drive 8 into the differential drive 9. Bythe present configuration of the drive unit 4 with a first gear stage 7in form of a belt transmission, a second gear stage 9 as a planetarydrive with a sun gear 20 as an input element, with a rotationally fixedsupported ring gear 19 and the planet carrier 23 as the output element,a transmission ratio to the slower can be achieved of less than 20, i.e.i<20. In this case, the achievable transmission ratio depends on thediameter ratio between the driving wheel 10 and the output wheel 12 aswell as on the number of teeth of the wheels 19, 20, 23 of the planetarydrive 8. Depending on the diameter ratio or the number of teeth ratio,the drive unit 4 can be formed such that the differential carrier 26rotates up to 20-times slower than the driving shaft of the electromotor 3. In the present embodiment with a belt drive 7, the internalchamber of the drive portion 11, in which the belt drive 7 is arranged,is dry, which means no lubrication is necessary here. Only the driveportion 14 is filled with lubricant for cooling or lubricating theplanetary drive 8 and the differential drive 9.

FIG. 2 shows an electric drive 2 according to a second embodiment. Thisembodiment generally corresponds to the embodiment shown in FIG. 1, sothat concerning the common features, it is referred to the abovedescription. In this case, the same components are provided with thesame reference numerals and changed components are provided withreference numerals increased by the numerical value 100.

The only difference between the present embodiment and that shown inFIG. 1 is, that the first gear stage 107 is formed as a chain drive,which has a driving wheel 110, an output wheel 112 and a continuouschain 113 for the transmission of the torque by the driving wheel 110onto the output wheel 112. As a chain drive is used as the first gearstage 107, the whole drive unit 4 can run for cooling or lubrication ina joint oil bath within the stationary housing 17. Special seals betweenthe housing portion 11 for the chain drive 7 and the housing portion 14for the planetary drive 8 or the differential drive 9 are not necessary.

With the present embodiment with a chain drive 107, a transmission to aslower speed can be achieved with a transmission ratio of up to 20, i.e.i<20.

FIG. 3 shows an electric drive 2 according to a third embodiment. Thisembodiment generally corresponds to the embodiment depicted in FIG. 2,so that concerning the common features, it is referred to the abovedescription. In this case, the same or corresponding components areprovided with the same reference numerals and changed components areprovided with reference numerals again increased by the numerical value100.

The only difference between the present embodiment and that shown inFIG. 2 is, that the first gear stage 207 is formed as a single-step spurgear drive, which transmits the torque, introduced by the electric motor3, to the hollow shaft 24.

The spur gear drive 207 comprises a first toothed wheel 210, which isalso designated as the driving wheel, and a second toothed wheel 212,which is meshing with the first toothed wheel 210 and can also bedesignated as the output wheel. It is visible, that the second toothedwheel 212 is connected in a fixed manner to the hollow shaft 24 for thetorque transmission. The two toothed wheel 210, 212 are, especially,formed as spur gears, preferably with helical gearing.

The number of teeth of the two toothed gears 210, 212 is selected such,that with the drive unit 4 according to the present embodiment betweenthe electric motor 3 and the differential carrier 26, a transmission tothe slower with a transmission ratio of smaller than 20 is achieved,(i<20), i.e. the differential carrier 26 rotates slower than the outputshaft of the electric motor 3. As in the embodiment of FIG. 2, also inthe present embodiment according to FIG. 3, no special sealing means arenecessary between the first housing portion 11 and the second housingportion 14. The drive unit 4 runs in a joint oil bath. The presentembodiment shows a single-stage spur gear drive 7 as a first drivestage. It is, however, clear, that the first gear stage, depending onthe required transmission ratio, can also be formed as a multi-step spurgear drive, which can have two or more spur gear pairs.

FIG. 4 shows an electric drive 2 according to a fourth embodiment. Thiscorresponds generally to that shown in FIG. 1, so that concerning thecommon features, it is referred to the above description. In this case,same or corresponding components are provided with the same referencenumerals and changed components are provided with reference numeralsagain increased by the numerical value 100.

The special features of the present embodiment are, that the planetarydrive 108 has two planetary gear stages 25, 25′, which selectively cantransmit the torque to the differential carrier 26, wherein the clutchassembly 42 is provided for switching the planetary gear stages 25, 25′.The two planetary gear stages 25, 25′ are arranged parallel concerningthe function, i.e. the torque introduced into the hollow shaft 24, istransmitted via the first planetary gear stage 25 or via the secondplanetary gear stage 25′ to the differential carrier 26. The firstplanetary stage 25 comprises a first sun gear 20, first planetary gears22, a first ring gear 19 and a first planet carrier 23. The secondplanetary gear stage 25′ comprises a second sun gear 20′, secondplanetary gears 22′, a second ring gear 19′ and a second planet carrier23′. It is visible, that the first gears 19, 20, 22 have differentdiameters and, thus, different numbers of teeth than the second gears19′, 20′, 22′. In this way, by means of the torque transmission via thefirst planetary gear set 25, a different transmission ratio can beachieved than in the torque transmission via the second planetary gearset 25′, so that the differential carrier 26 can be driven withdifferent numbers of revolution.

The first and the second sun gear 20, 20′ are connected so as to berotationally fixed to each other or to the hollow shaft 24, so that theyrotate with the same number of revolutions around the second rotationalaxis B. The first planetary gears 22 are connected via the first planetcarrier 23 to the differential carrier 26. Correspondingly, the secondplanetary gears 22′ are connected via the second planet carrier 23′ tothe differential carrier 26. Thus, the first planetary gears 22 as wellas the second planetary gears 22′ rotate together with the differentialcarrier 26 around the rotational axis B. The first and second internalgears 20, 20′ can selectively be supported on the housing 17rotation-wise or can be released thereto.

The clutch assembly 42 comprises in the present embodiment a switchingclutch. The switching clutch 42 can realize three switching positions,which are achieved by means of a transferable sliding sleeve 38. Thecontrol is carried out via an electronic control unit (not shown), whichcontrols an actuating device, which again transfers the switching clutch42, when required, into the required switching position.

In a first switching position, the first ring gear 19 is connected so asto be rotationally fixed to the stationary housing 17, while the secondring gear 19′ can freely rotate relative to the stationary housing. Inthis switching position, the torque transmission is achieved from thehollow shaft 24 via the first planetary gear stage 25 to thedifferential carrier 26. In this case, the present electric drive 2operates as in the embodiment of FIG. 1, wherein a reduction ratio canbe achieved of up to 20.

In a second switching position, the ring gear 19 is freely rotatablerelative to the stationary housing 17, while the second ring gear 19′ isconnected so as to be rotationally fixed to the stationary housing 17.In this switching position, the torque transmission is achieved from thehollow shaft 24 via the second planetary gear stage 25′ onto thedifferential carrier 26. Depending on the diameter ratio or the numberof teeth ratio, the gears 19′, 20′, 22′ of the second planetary gearstage 25′, transmission ratios of eight to fifteen can be achieved inthe second switching position, i.e., i=8−15. In this case, atransmission ratio of eight means, for example, that the differentialcarrier 26 rotates slower than the electric motor 3.

In the third switching position, the first ring gear 19 as well as thesecond ring gear 19′ are freely rotatable relative to the housing 17. Inthis switching position no torque is transmitted between the hollowshaft 24 and the differential carrier 26 or between the electric motor 3and the side shafts 5, 6. This is, for example, necessary, when themotor vehicle has to be towed during a breakdown.

FIG. 5 shows an electric drive 2 according to a fifth embodiment. Thisembodiment corresponds to a combination of the embodiments of FIGS. 2and 4, so that concerning the common features, it is referred to theabove description. In this case, the same or corresponding componentsare provided with the same reference numerals.

The present embodiment is characterized in that the first gear stage 107is formed as a chain drive, as in the embodiment of FIG. 2. Thus, thewhole drive unit 3 can run for cooling or lubrication in a joint oilbath within the stationary housing 17. Furthermore, a clutch assembly 42in form of a switching clutch is provided, as in the embodiment of FIG.4. The switching clutch 42 can, selectively, connect the first ring gear19 (first switching position) or the second ring gear 19′ (secondswitching position) rotationally fixed to the stationary component 17for supporting a torque or can be released relative thereto (thirdswitching position). In the first switching position, a transmissionratio of up to 20 can be achieved. In the second switching position,depending on the number of teeth of the gears of the second planetarygear set 25′, transmission ratios of 8 to 15 can be achieved, i.e.i2=8−15.

FIG. 6 shows an electric drive 2 according to a sixth embodiment. Thisembodiment generally corresponds to a combination of the embodiments ofFIGS. 3 and 5, so that concerning the common features, it is referred tothe above description. In this case, same or corresponding componentsare provided with the same reference numerals. Changed components areprovided with reference numerals which are again increased by thenumerical value 100.

In the present embodiment, the first gear stage 207 is formed as asingle-stage spur gear drive, as it is shown in FIG. 3. It can beunderstood, however, that the first gear stage could also be formed as abelt drive of FIG. 1 or as a chain drive of FIG. 2. Further, it isvisible, that a clutch assembly 142, similar to the embodiment of FIG.5, is provided on the planetary drive 108.

A special feature of the present embodiment of FIG. 6 is that the clutchassembly 142 comprises a first friction clutch 43 and a second frictionclutch 44, arranged axially next to each other.

The first friction clutch 43 is arranged in the power path between thefirst ring gear 19 and the stationary housing 17. The second frictionclutch 44 is arranged in the power path between the second ring gear 19′and the housing 17. The two friction clutches 43, 44 may be formed asfriction disk clutches. The first friction clutch 43 comprises a clutchinput element 45, which is connected so as to be rotationally fixed tothe first ring gear 19, a clutch output element 46, which is connectedso as to be rotationally fixed to the housing 17, as well as a diskpack, which is arranged operationally between the clutch input element45 and the clutch output element 46. The second friction clutch 44comprises a clutch input element 47, which is connected so as to berotationally fixed to the second ring gear 19′, a clutch output element48, which is connected so as to be rotationally fixed to the housing 17,as well as a disk pack, which is arranged operationally between theclutch input element 47 and the clutch output element 48. The twofriction clutches 43, 44 are axially supported on a pressure plate 35,which is connected in fixed manner to the housing 17.

For actuating the first friction clutch 43, a first actuating device 33is provided, which is represented schematically by a piston. Foractuating the second friction clutch 44, a second actuating device 34 isprovided, which is also represented schematically as a piston. The firstor second actuating device 33, 34 are not limited to hydraulicactuators, but can have any form, for example also be in form ofpneumatic, electromechanical or electro-magnetic actuators. The twoactuating devices 33, 34 are controlled, as required, by a centralcontrol unit (not shown). By using two friction clutches 43, 44 and twoseparate actuating devices 33, 34, the two friction clutches 43, 44 canbe controlled individually or independently of each other. The to betransmitted torque can be variably adjusted in dependency of the closedposition of the corresponding friction clutch 43, 44 between a closedposition, in which the whole torque is transmitted, and an openposition, in which no torque is transmitted.

With the present embodiment with a spur gear drive 207 and a clutchassembly 142 with two friction clutches 43, 44, a transmission, as inthe embodiments of FIGS. 4 and 5, can be achieved, which, respectively,have a switching clutch, i.e., when the first friction clutch 43 iscompletely closed and the second friction clutch 44 is completely open,so that the first ring gear 19 is supported rotationwise on the housing17, a first transmission ratio i1 is achieved, which is smaller than 20(i1<20), i.e. that the differential carrier 26 rotates slower than theelectric motor 3.

If vice versa, the first friction clutch 43 is completely open and thesecond friction clutch 44 is completely closed, so that the second ringgear 19′ is decelerated relative to the housing 17, a secondtransmission ratio i2 is achieved, which is smaller than the firsttransmission ratio i1 and can, especially, be between eight and fifteen(i2=8−15), i.e. that the differential carrier 26 rotates slower than theelectric motor 3 (between ⅛ to 1/15 of the rotational speed of theelectric motor 3). By means of corresponding control of at least one ofthe two friction clutches 43, 44 in the intermediate positions, also anyother transmission ratio can be adjusted, which is between the maximumand the minimum transmission ratio. Especially, with the presentembodiment, a load uninterrupted switching is possible. The switchingcan be carried out under load quickly and comfortably.

The electric drives 2 according to the above described embodiments havethe advantage of a compact configuration, as the second and third gearstage, i.e. the planetary drive 8, 108 and the differential drive 9 arearranged coaxially to each other. The axle off-set, provided between theelectric motor 3 and the second or third gear stage 8, 108, 9 is bridgedby the first gear stage 7, 107, 207, which produces a transmission to aslower speed. Depending on the configuration of the first gear stage 7,107, 207 or by means of providing a clutch assembly 42, 142, severaldifferent transmission ratios can be realized. This enables again anoptimal adjustment between the electric motor 3 and the drive unit 4.

1. An electric drive for a motor vehicle, comprising: an electric motorand a drive unit, wherein the drive unit has a first gear stage,driveable by the electric motor, a second gear stage, driveable by thefirst gear stage and a differential drive, driveable by the second gearstage, wherein the first gear stage has a driving wheel and an outputwheel, wherein the driving wheel is arranged coaxially to an outputshaft of the electric motor and is rotatingly driveable by the electricmotor around a first rotational axis, and wherein the output wheel isdrivingly connected to the driving wheel and is rotatingly driveablearound a second rotational axis (B), wherein the second rotational axis(B) is arranged so as to be parallel off-set to the first rotationalaxis (A), and wherein the second gear stage and the differential driveare arranged coaxially to the second rotational axis.
 2. An electricdrive according to claim 1, wherein the first gear stage comprises areduction drive, which is formed one of a belt drive, a chain drive or aspur gear drive.
 3. electric motor according to claim 1, wherein thesecond gear stage comprises a planetary drive with a ring gear, a sungear, a multitude of planetary gears, and as well as a planet carrier,wherein, especially, one of either the, sun gear or the ring gear, isrotatingly driveable by the output wheel of the first gear stage aroundthe second rotational axis (B).
 4. The electric drive according to claim3, wherein the sun gear is drivingly connected to the output wheel, andthe ring gear is supported or supportable on a first stationarycomponent against rotation, and the planet carrier is drivinglyconnected to the differential drive.
 5. The electric drive according toclaim 3, wherein the differential drive has a differential carrier,which is rotatingly driveable by the planet carrier around therotational axis (B).
 6. The electric drive according to claim 5, whereinthe planetary drive and the differential drive are arranged axially nextto each other.
 7. The electric drive according to claim 4, whereinbetween the ring gear of the planetary drive and the stationarycomponent, an externally controllable clutch assembly is provided thatis configured to selectively connect the ring gear to the stationarycomponent in a rotationally fixed manner or release the ring geartherefrom.
 8. The electric drive according to claim 7, wherein: anactuating device for actuating the clutch assembly is provided.
 9. Theelectric drive according to claim 1, wherein: the planetary drive has afirst planetary gear stage with a first transmission ratio between aninput element and an output element and a second planetary gear stagewith a second transmission ratio between the input element and theoutput element.
 10. The electric drive according to claim 7, wherein:the clutch assembly is formed such, that, selectively, the ring gear ofthe first planetary gear stage or the ring gear of the second planetarygear stage can be supported on the stationary component against rotationor can be disconnected.
 11. The electric drive according to claim 7,wherein: the clutch assembly comprises a switching clutch, which istransferable at least into a first switching position and into a secondswitching position, wherein in the first switching position of theswitching clutch, the ring gear of the first planetary gear stage isconnected so as to be rotationally fixed to the stationary component andthe ring gear of the second planetary gear stage can rotate freelyrelative to the stationary component, and wherein in the secondswitching position of the switching clutch, the ring gear of the firstplanetary gear stage can rotate freely relative to the stationarycomponent and the ring gear of the second planetary gear stage isconnected rotationally fixed to the stationary component.
 12. Theelectric drive according to claim 11, wherein: the switching clutch istransferable into a third switching position, in which the first ringgear and the second ring gear are freely rotatable relative to thestationary component.
 13. The electric drive according to claim 7,wherein: the clutch assembly comprises a first friction clutch, which isarranged between the first ring gear and the stationary component, and asecond friction clutch, which is arranged between the second ring gearand the stationary component.
 14. The electric drive according to claim13, wherein: the first and the second friction clutch are each variablycontrollable between an open position, in which the torque transmissionis interrupted, and a closed position, in which torque is transmitted.15. The electric drive according to claim 7, wherein: for each of thefirst and the second friction clutch, a separate actuating unit isprovided, which can individually actuate the corresponding frictionclutch.
 16. (canceled)